Variable speed control for winding machines



Dec. 29, 1959 J. R. LONG VARIABLE SPEED CONTROL FOR WINDING MACHINES 4 Sheets-Sheet 1 Filed Jan. 22, 1957 INVENTOR: Io H N R. LONG,

ATTORNEYS Dec. 29, 1959 J. R. LONG 2,918,779

VARIABLE SPEED CONTROL FOR WINDING MACHINES 4 Sheets-Sheet 2 Filed Jan. 22, 1957 JOHN R. LONG,

INVENTOR @Im V 74 by mew, km 2215;,

I'Z.O-

I24" BY 1 ATTORNEYS Dec. 29, 19-59 J. R. LONG VARIABLE SPEED CONTROL FOR WINDING MACHINES Filed Jan. 22, 1957 4 Sheets-Sheet 3 \06 INVENTOR:

J'oH N R. Lo N6.

ATTORNEYS Dec. 29, 1959 J. R. LONG 2,918,779

VARIABLE SPEED CONTROL FOR WINDING MACHINES Filed Jan. 22, 1957 4 Sheets-Sheet 4 INVENTOR Ionu R. LONG f1 g= 7 E BY5J3 MgM+W ATTORNEYS United States Patent VARIABLE SPEED :CONTROL lFGR WINDING MACHINES -'John R. Long,'-'Hickory,'N;C., assignortoShuford Mills,

Inc.,Hick'ory, Nic acorporation of'North Carolina Application January 22, 1957, Serial No. 635,346

18-Claims. (CI. 5798) This invention relates to machines havingmeans for traversing yarnonto yarn carriers and particularly to spinning machines, twisting machines and other winding .machines characterizedby: rings movable with a traversing ring rail for winding yarn on yarn carriers such as bobbins, spools and the like. The .present invention is disclosed in association witha spinning machine, although it is to be understood that -the present invention may be readily adapted to other types of winding machines.

This application isa continuationin part of my co- ,pending application-entitled, SpeedControl for Winding :of the traversing mechanism for varying the speed of the machinein .a filling wind whereby the machine-op- .erates at .a predetermined relatively high speed during of the yarnuat the relatively large diameter of ,"thepackage and operates.at.,a.relatively. slow' speed during winding of the yarn ata relatively ,small diameter of V the package.

7 It .is .well known that the distance between the usual ring-traveler and the bobbin when initial turns of yarn are being wound thereonismuch greater than it is when ,a relatively large number of turns of .yarn has been wound von thebobbin so that, in machines which are driven at ,a:constant speed, there is .amuch greater drag placed on the yarn by the traveler when the packageis of relatively small diameter, or only a relatively few turns of yarn are wound on the bobbins, as compared to the drag on the yarn when a substantial number of turns of yarn have been wound on the bobbins, with the result that the yarn is relatively taut as it is initially being woundon .the bobbin and, the tautness of the yarn gradually diminishes as the'diameter of the package increases. reason, it has been necessary, heretofore, to operate spinning machines and the like :at relatively slow speeds in order to avoid placing excessive tension on the yarn For this duringthe initial winding of yarn on the bobbin However, by providing means whereby the speed of the machine may be varied in the course of each reciprocation of the yarn traversing means or ring rail, this enables substantially higher production.

It is another object of this invention toprovide means under control of the traversing mechanism or builder motion for gradually increasing the speed of the machine in the course of each downwardstroke of the ring rail and for gradually decreasing the speed of the marchine'duringeach upward stroke of the ring rail during a filling :WjIldw. This risaccomplished by correspondingly 2,918,779 Patented Dec. 29, 1959 "ice gradually changingthepressure admitted to a fiuid oper- ,ated variable vspeed drive mechanism for the machine.

'It'isjanother object ofthis invention to provide a meth- .od :and apparatus of the character described with means to maintain the speed of the machine relatively slow during agiven number of reciprocations of the ring rail upon thestarting of thefilling wind; that is, during the winding of the bunches on the lower-portions of straight bobbins. Thereafter, the-speed of the machine gradually increases with. each downward stroke ofthe ring rail and ,graduallyvdecreases with each upward stroke of the ring rail. 7

Some of the objects of the invention having been stated, other objects will appear as the'description pro- .ceeds 'when taken in connection with the accompanying drawings, in which-- Figure .1 is a somewhat schematic .side elevation of a spinning machine embodying the.present invention;

Figure 2.is a fragmentaryelevation, partially in section, taken substantially along line 2-2 in Figure .1;

Figure} is an elevation, partially in section, taken substantially alongline 3-3 in Figure .1;

Figure 4 is an elevation of the valve assembly shown [in the lower left-hand portion :of Figure 1, and showing the operatingparts thereofin longitudinal section, the -valvekassernbly being closed;

Figure .5 is an enlarged longitudinal sectional view .through the variable speed pulley assembly shown in the upper left-hand portion of Figure 1 and showing the same ,as thoughthe valve .assembly of Figure 4'is'open;

' Figure '6 shows amodified form of the invention illus- 'trati ng-a portion of the opposite side of a machine such ,as ,is shown in Figure l with parts broken away and showing, in .particular,; the means for-maintaining relatively slow operation of the machine during the building .of the bunch about each'of the bobbins;

Figure 7 is aschematic diagram :of the constant speed electrical control circuit.

Referring more specificallyto the drawings, the mach ine.shown comprises drafting rolls L0 supported on roll ,stands llfixed to a beam 12 spaced above a spindle'rail I3. The beam 12 and spindlerail-1-3 are supported, at opposite ends thereof, onhea d-end and foot-end frame ,members :14 and 15. A maincylinder-shaft 16 is jour- ,naled in the, frame members 14, .1-5 and has a cylinder 17 thereon which drives belts or tapes 20 which, in turn,

. impart. rotation to spindlesll at opposite sides'of the machine. :The spindles are supported bythe spindle rails .13 have corresponding yarn carriers, bobbins or spools .22 mounted thereon about each of which yarn Y is woundto form a yarn package 23.

The machine includes a vertically reciprocable ring .rail24 mounted on each sidethereofwhich supports a plurality of rings 25 which encircletheyarn packages 23,

and each of which has atraveler 26 thereon for guiding the corresponding yarn from the drafting rolls 10 onto the corresponding bobbin 21. In its course from the drafting :rolls 10 to the corresponding bobbin, each strand 1 of yarn Y passes through a suitable guide 27 so the yarn balloons as it is guidedthrough the corresponding traveler and inwardly to the corresponding bobbin.

The maincylinder shaft 16 drives the drafting rolls 510, through conventional mechanism enclosed in the head- .end frame member 14, .and also drives: a builder motion for reciprocating thering rail 24. The builderv motion is best shown in Figure 2, this builder motion being of the conventional type used for building a filling wound package. That is, with each cycle of machine, the ring IHllS commence directing the yarn to the bobbins while in a relatively low position and the length ofeach vertical stroke thereof is substantiallythe same throughout formation of the packages 23. However, the ring rails are progressively stepped upwardly so that, with each upward stroke of each ring rail 24 the diameter of the packages gradually decreases and, conversely, with each downward stroke of each ring rail 24, the diameter of the packages gradually increases and, ultimately, the upper end of each package of yarn is tapered substantially as shown in Figure 1.

The builder motion, broadly designated at 30, may be of a type which includes a cam 31 driven to rotate continuously by conventional means, not shown, and which is engaged by a follower 32 projecting from a lever 33 pivotally mounted, as at 34, on the head-end frame member 14. A rack 35 carried by lever 33 has a roller or follower 36 thereon which engages a curved cam surface 37 on an auxiliary lever or builder arm 40 also pivotally supported at 34. The rack 35 is shifted, in a step-bystep manner, to gradually change the range of movement of the arm 40, although the length of each stroke of the free end of the arm 40 remains substantially constant, all of which is well known in the art.

The end of the lever 33 remote from the rack 35 preferably has a suitable weight 41 thereon to assist in maintaining the follower 32 in engagement with the lower surface of the cam 31. The cam surface 37 on the arm 40 is maintained in engagement with the follower 36 by the weight of the ring rail and intervening parts. These intervening parts may include a chain or pliable element 43, one end of which is connected to the free or forward end of the arm 40. The pliable element 43 extends upwardly and passes over a suitable guide means 44 carried by the head-end frame member 14 and the other end of the pliable element is connected to an arm 45 (Figure 1) whose lower end is fixed on a rocker shaft 46 journaled in brackets 47 depending from the spindle rails 13.

The rocker shaft 46 also has a lifter arm or lever 50 fixed thereon beneath each of the spindle rails 13, and one end of which has a follower or roller 51 thereon upon which rests the lower end of a corresponding lifter rod 52. A plurality of said lifter rods 52 is provided at each side of the machine and these lifter rods are guided for vertical movement in the corresponding spindle rails 13 and support, at their upper ends, the ring rails 24. The lifter arm or lever 50 is also provided with a weight 53 which, with other similar weights, not shown, normally urges the corresponding ring rail 24 upwardly, as is conventional, and thereby maintain the curved surface 37 (Figure 2) of the builder arm 40 in engagement with the follower 36 of the builder motion 38. Since the builder motion 30 and the other parts of the machine heretofore described are conventional, a further detailed description thereof is deemed unnecessary. It is with a machine substantially of the character thus far described that the present invention is particularly adapted to be associated.

It is a well known practice to drive spinning machines and the like by means of an electric motor, such as the motor indicated at 60 in Figures 1 and 3. However, the electric motor 60 is preferably mounted in the manner shown in the present drawings or in substantially the manner shown in said copending application so the motor 69 may move toward and away from the main shaft 16 of the machine as the effective diameter of a variable speed pulley assembly 61 is varied in a manner to be later described during reciprocation of the ring rail 24. The motor employed is preferably of the constant speed type and the variable speed pulley assembly 61, mounted on the shaft 62 of the motor 60 (Figure is preferably of a type such as is disclosed in my copending application, Serial Number 418,536, filed March 25, 1954, now Patent No. 2,810,296. The pulley assembly 61 may be mounted on either shaft 62 or 16 without departing from the spirit of the invention. The electric motor 60 may be'connected to a suitable source of electrical energy by t means of a pair of conductors 63, 64 having a plug or electrical connector 65 on the free ends thereof. The conductor 63 may have a manually operable switch 66 interposed therein for controlling the flow of current to the electric motor 60.

The electric motor 60 is fixed on a pivoted support shown in the form of a pair of arms 70 (Figures 1 and 3), corresponding ends of which are pivotally mounted on a horizontal shaft 71 carried by the foot-end frame member 15 and an outboard frame member or standard 72. The main cylinder shaft 16 has a pair of V-pulleys 74 fixed thereon and endless V-belts 75, 76 connect the pulleys 74 with the variable speed pulley assembly 61. In order to maintain the belts 75, 76 taut and thereby insure that the desired changes are made in the speed of the machine as the effective diameters of the pulleys of the pulley assembly 61 are varied, the free ends of the motor supporting arms 70 are resiliently supported by respective tension springs 77. There are two such springs 77 shown in Figure 1, the lower ends of the tension springs 77 being connected to the free ends of the corresponding motor supporting arms 70. The upper ends of the tension springs 77 are connected to a bracket 80 carried by a post 81 whose lower end is fixed to the standard 72 (Figure 3). Although not limited thereto, the pulley assembly 61 is shown as being of a type disclosed in my said copending application, Serial Number 418,536 and, accordingly, only so much of the variable speed assembly 61 will be described as is necessary to a clear understanding of the present invention.

The variable speed pulley assembly 61 (Figure 5) comprises a sleeve 82 which is fixed on the motor shaft 62, as by a key 83 and set screws 84. A second sleeve or tubular hub 85 is keyed, as at 86, for axial movement on the sleeve 82. The hub 85 has four cones or inclined flanges 87, 88, 89 and thereon. The belt 75 is entrained over the pulley A formed of flanges 87, 88 and the belt 76 is entrained over the pulley B formed of flanges 89, 90. Flange 87 is fixed to or formed integral with the inner end of the hub 85 and the flange 89 is fixed on the hub 85. The two flanges 88, 90 are keyed, as at 91, for axial movement on the hub 85 and relative to the corresponding mating flanges 87, 89.

The flanges 8'7 and 89 are held in fixed relation with each other by means of a plurality of bolts 92 which loosely penetrate the flange 87 therebetween, only one of the bolts 92 being shown in Figure 5. The flanges 88, 98 are prevented from moving apart from each other, to cause them to move together axially of the hub 85, by means of a plurality of circularly spaced bolts 93, which loosely penetrate the flange 89 therebetween. Only one of the bolts 93 is shown in Figure 5. The bolts 93 also prevent relative rotational movement between the flanges 88, 90.

The outer end of the flange 90 is engaged by a plurality of circularly arranged legs or piston rods 101 which loosely penetrate the closed inner end 96 of a cylinder 182 and are fixed to a piston 103 movable within the cylinder 102. The inner end 96 of the cylinder 102 is fixed on the end of the hub 85 remote from the flange 87 so the flanges 87, 89 are maintained in fixed relation with the cylinder 182. The cylinder 102 is provided with a flexible diaphragm 105 whose outer edge is fixed to the outer end of the cylinder 102 by a plurality of screws 106 which are also used for securing a cylinder head or outer closure 107 against the outer end of the cylinder 102.

A pipe fitting 110, which is shown as being substantially L-shaped in Figures 1 and 5, is connected tothe central portion of the cylinder head 107, for communication with the interior of the cylinder 102, in such a manner as to form a rotary connection between the cylinder head 107 and the fitting 110, since the cylinder 102 rotates with the pulley assembly while the fitting 110 does not rotate. To this end, it will be noted that the mp 124 interposed "therein. valve 120 may be of conventional or ,any desired coninnerendpf the rfittingllt) ,is ,fixed as by a pressedfit, in the inner races of antifr'iction .or ballb ng 1.1.1 i posi'tio'ned in the cylinderfhead 1,07 and 'thehtting L110 extends outwardly from the bearings 1,11 and loosely Ithroughan opening 112 formedlinThead 107. ,A suitable seal or O-ring [113 mayibeprovided between the fitting 110an'd .the wall-of the opening'lIZ to .prevent leakage of pressure from within the cylinder102.

From the foregoing, it is apparent that, ,when the ,;'p1illeys A, B occupy the positioiishownlin Figure 5 and .lfluidpressure isreleased from cylinder 102, the tension in the'belts 75, .76 forces the flanges-81, 89 away from the "respective 'flanges 88, 90 and/or vice versa, thereby re- .ducingthe effective diameter of .thepulleys A, B. Conversely, when pressure is introduced intocylin'der 102, Ihe cylinder 102 exerts apulling 'force on hub 85 and flanges 87 89 wh'ilethe'piston 103 and piston rods 101 exert apushing force against the flanges 88,90. This causes .tlie-motor160 and pulleyrassembly 61 to move toward-the pulleys 74, due to-"the-tension in the belts 75, '7 6, thereby increasing the effective diameter of the pulleys ,QA,,B of the assembly 61.

' fTheinvention resides in the combinataion with a vari- ..air .system to the cylinder 102' and wherein means are provided whereby the amount of pressure inthe cylinder 102 isgradually decreased to a predetermined minimum with each upward stroke of the ring rail 24 and the pres- ..sure admitted to ,the cylinder 102 is gradually increased with each downward stroke of the ring ra'il24'. As here- .toforestated, a decreasein pressure in thecylinder102 decreases thekeffect'ive diameter of lthepulleys A, Band .therebyfdecreases the speed of the machine, while an increase injpressure in the cylinder 102 serves toincrease the e'lfective rliame ter'of the pulley assembly 61 to there- "by proportionally increase the speed of the machine.

'It will be observ'edin Figuresl and 5 that the pipe fitting 110 serves to communicatively connect one end of a Iconduitor fluid pressure 'line 115 to the cylinder 102 and the other end of conduit 115 is connected to one side of .a, pressure control or regulator valve broadly designated 312,120 (Figures 1 and 4) which is 'fixed,'by means -;of abracket 121, .tothe foot-end frame member 15. The other. side of the pressure regulator valve. 120 has one of acon'duitor pressure line 122 connecte'dthereto which ,eiitends from a suitable source of .fluid pressure, not' shown, .such as compressed air. The conduit 122 prefer- ,ably has .a manually operable shut-off valve 123 and a The pressure regulator .struetion. However, in order'that the intricacies of the present inventionmay be,clear ly understood, a somewhat detailed description of the pressure regulatorvalve 120 willnow be given.

The pressure regulator valve 120." is shown in'the form ,of a hou ing Comprising afront or primary part 130 anda rear or secondary part Q13-1havin'g a'flexible diaphragm129'fixed therebetween. A .pairof valve plungers are mounted for relativecoaxial movement in the :housing'of the --valve 120, thefront or primary valve plungerbeing indicated at 132 and the rear. orsecondary valve plunger being indicatedat 133. Both. of the valve plunger s 132,,- 133 are of hollow construction.

One end .of a relatively heavy regulator spring 134 bears against (the inner valve plunger 133. The .pressure 10f spring134 against'the valve,plun'ger'."133 and diaphragm 129 is manually controlled by means of an adjustment screw'135. Thehousing part 130 o'frthe regulator 'valve 120 has a sleeve tor tubular guide '136 fixed thereinin which the outer or .front valve plunger '132 is mounted for' longitudinal sliding movement, said outer valve plunger 132 being reduced at .its outerrendtan'd looselypene- 'trating thecorresponding end of sleeve 136 to form a shoulder 137 on the outer valve plunger 132 for limiting outward movement thereof. A compression spring 140 normally urges the shoulder 137 against'the restricted end of the sleeve 136, the endof thespring 140 opposite from the outer plunger being seated against'the; corresponding end of the innerplunger 133. The left-hand end of plunger 133 is loose-in-the sleeve 136 so that a'ir may pass therebetween. I

-more passagewaysh therein-for establishing communication between the passageway fandthe valve seat a, while the portion of the-valve plunger 132 tothe right of the enlarged 'portionlg thereofinFigur-e 4 has oneormore passageways jtherein establishing communication betweenthe passageway e and the linterior of the right- 'hand portion ofQtheoutervalve plunger 132. The right- '-hand housing part 131 o'f-thepressure regulator valve 120 has an opening 143 therein which communicates with the atmosphere and the right-hand end of theinner plunger'133 also has openings k therein which communicate with the housing part'131.

'The pressure regulatoryalve1'20 is controlled byithe builder motion 30. .To this -end,-the :part 130 of-Lthe housing 'of pressure regulator valve120 has one endrof a control lever 150 pivotally connected :thereto whose medial portion is adapted toengage-theouter end ofithe outer plunger 132. The otherend of the control lever 150 has one end of acable-orpliable element15'1'rconnected thereto (Figure 1) which-extends longitudinally of the machine and'passesiunder and'oversrespective guides or-rollers 152, 153 (Figure 1 and 2) and then downwardly where it is connected-to the'rearend of the lever 33 of the builder motion 30. The rollers 152,

153 are suitably journaled on a bar or frame member 155 and one of the spindle-rails13. The bar 155 is suitably secured toand dependsfromthe corresponding spindle rail 13. The cable 151 preferably has a tension spring 154 interposed therein.

Since the left-hand end of the builder motion lever 33 (Figure 2) moves upwardly .with each ldownward stroke of each ring rail 24, therearor right-hand end of. the lever moves downwardly, placingithe spring'..1-54 .under 'tension and gradually moving thenvalve control lever 150 in a clockwise direction in Figures l and 4jt'o gradually open the pressure regulator-valve 120. In'so doing, the pressure in the cylinder 102 of thevariable speed pulley 61 is gradually increased, thereby gradually vincreasing the effective diameterof the pulleys Aand. B. The manner in which the valve operates will .be later described. I

- On the other hand, as the .cam1'31 'f vthtabtrildernmtion 30 moves thelever 33 downwardly at its left-hand endv in Figure 2,..this raisesthe ring rail 24 as. the cable 151 and. spring .154.,are relaxed, thereby permitting the valve control lever 150 to arages gradually move outwardly to closed position. It is apparent that this gradually reduces the pressure in the cylinder 102.

Due to the tension springs 77 lifting the motor 70,

when the pressure in the cylinder 102 is lowered, the belts 75 exert sufficient pressure on the proximal inclined surfaces of the respective flanges 87, 88 and 89, 90 to cause the respective flanges to move apart from each other and thereby reduce the efiective diameter of the pulleys A, B formed from these flanges. When the effective diameter of the pulleys A, B is decreased, the machine is driven at a relatively slow speed and, as the effective diameter of the pulleys A, B is increased, the speed of the machine is proportionately increased.

It is thus seen that, with each upward stroke of the ring rail 24, the speed of the machine is gradually decreased to avoid placing the yarn under excessive tension and, as the ring rail 24 moves downwardly, the speed of the machine is gradually increased so the yarn does not become unduly slackened as the diameter of the yarn packages 23 increases relative to the rings 25. This insures that the yarn is of more uniform tension throughout each package 23 and is more tightly wound on each package so that each package actually contains more yarn than would be the case if the machine operated at a constant speed. Also, by varying of the speed of the machine with each stroke of the ring rail according to the present invention the overall speed of the machine may be relatively higher than has been possible heretofore. This is due to the fact that, heretofore, the speed of the machine was limited only to the maximum tension that could be placed on the yarn during the winding of the coils of small diameter about the spool or bobbin.

The filling-wound packages 23 shown in Figures 1 and 2 are shown as being straight at the lower portion thereof, as would be the case in the event of the bobbins or yarn carriers each having a cone-shaped or tapered lower portion about which the yarn is initially wound. However, it is not unusual to form filling-wound packages on 1 straight bobbins or yarn carriers as shown in Figure 6.

In the modified form of the invention shown in Figure 6, those parts shown therein which are identical to corresponding parts shown in others of the drawings will bear the same reference characters with the prime notation added. It is to be understood that the structure for controlling the ring rail during the bottom portion of its traverse (Figure 6) is used in association with the structure shown in Figures 1 through 5, but is used only in the event that bobbins or yarn carriers are not equipped with a cone-shaped or tapered lower portion.

If so desired, the operator may disconnect the cable 151 from the builder motion lever 33 during the forming of the bunches at the lower portions of the yarn carriers so the pressure regulator valve 120 will then remain open. However, the structure shown in Figure 6 causes the air to be exhausted from the cylinder 102 automatically during the traversing of the ring rail in the forming of the bunches on the lower portions of the yarn carriers.

To this end, an auxiliary control valve 160, shown in the form of a solenoid-operated valve, is interposed in the conduit 122' at a point between the source of pressure and the pressure regulator valve 120'. The solenoid valve 160 may be of any desired or conventional structure and is shown schematically in Figure 7 wherein it will be observed that the housing thereof is provided with inlet and outlet ports 161, 162 with which the corresponding portions of the conduit 122 communicate, and the housing of valve 160 is also provided with an exhaust port 163. A valve plunger or core 164 is mounted for vertical movement in the housing of valve 168 and is provided with a pair of passageways 165, 166 therein.

' The valve 160 is normally closed, at which time the passageway 166 establishes communication between the outlet port 162 and the exhaust port 163 to exhaust corripressed air from the pressure regulator valve The upper portion of the valve core 164 is reduced and is encircled by a solenoid coil 167, to opposite ends of which electrical conductors 170, 171 are connected. The passageway 165 is so located that, when the coil 167 is energized and the valve is open, the passageway is alined with the inlet and outlet ports 161, 162 to thereby admit fluid pressure to the pressure regulator valve 120 The conductor 170 extends to one side of a suitable source of current embodied in a plug 172, to the other side of which a conductor 173 is connected. The conductors 171, 173 lead to opposed terminals of a switch, generally designated at 175, suitably secured to the foot-end frame member 15 (Figure 6), as by means of a bracket 176.

A movable element or bus bar 177 is suitably supported for movement into and out of engagement with the terminals of the switch 175. In this instance,'the housing of switch has a shaft or bar 180 fixed therein on which the bus bar 177 is slidably mounted. The bus bar 177 has one end of a switch lever 181 pivotally connected thereto which extends upwardly through a suitable opening provided in the upper wall of the housing of switch 175 and whose medial portion is pivotally mounted, as at 182, on the housing of the switch 175. The upper end of lever 181 is slotted, as at 183, and the slot 183 is loosely penetrated by a connecting rod or link184. The link 184 has a pair of relatively adjustable stops 185, 186 fixed thereon which are positioned astraddle the upper portion of lever 180 and are adapted to alternately engage, and thereby impart movement to, the lever 181 with movement of the connecting rod or link 184.

Referring to Figure 6, it will be observed that thearm 45 has an extension 187 thereon which is loosely penetrated by the rod 184. The left-hand portion of the rod 184 in Figure 6 is encircled by a compression spring 190, one end of which is adapted to bear against the extension 187 of arm 45' and the other end of which bears against an adjustable stop or retainer 191 adjustably mounted on the rod 184.

Now, it is apparent that the builder motion, such as the builder motion 30 shown in Figure 2, will impart reciprocatory movement to the arm 45 as the ring rail 24 is reciprocated and effects progressive movement of the arm 4-5 in a counterclockwise direction in Figure 6 during reciprocation of the arm 45, although the arm 4-5 moves in strokes of substantially uniform length during each reciprocation thereof. Accordingly, during the traverse of the ring rail 24- adjacent the lower portions of the bobbins 22, the spring 190 may not engage extension 187 or, at least, the pressure exerted on the link or rod 184 by the compression spring 190 is negligible. Also, the distance between the stops 185, 186 relative to the switch lever 181 is such that the switch 175 will remain open during a predetermined number of reciprocations of the ring rail 24' so the valve 160 remains in its normal closed position and exhausts compressed air from the pressure regulator valve 120 to, in turn, permit compressed air to be exhausted from the cylinder 102'. It is apparent that the machine will then operate at a relatively slow speed; during the building of the bunches on the lower portions of the straight bobbins 22'.

Upon a predetermined number of reciprocations of the ring rail 24', the stop 186 on the link 184 engages and imparts counterclockwise movement to the lever 181 to close the switch 175 and open the solenoid valve 160, whereupon the machine functions throughout the remainder of the wind in the manner described with respect to the original form of the invention shown in Figures 1 through 5. The spring 190 permits the arm 45' and its extension 187 to move a substantial distance in a counterclockwise direction in Figure 6 after the stop 186 has engaged and imparted movement to the switch lever 181.

When the winding cycle has been completed and the builder motion, such as builder motion 39, is wound back 9 in the usual manner preparatory to initiation of another cycle in the operation of the machine, the switch lever .181 maybe manually returned. to open position or a spring, such as that indicated at 192, may be provided for returning the switch lever 181 to open position. Also, the switch 175 may be in the form of .a toggle switch so it will remain in closed or opened position when moved to either of these positions by the stops 185, 186.

In order that the manner in which variation in the pressure in cylinder 102 of the variable speed pulley assembly 61 is effected maybe clearly understood, a description of the operation of the pressure regulator valve 120 will now be given. f

When the regulator valve 120 is closed, the'parts thereof occupy substantially the position shown in Figure, 4 and, at this time, the pressure regulator spring 134 is under relatively 'light compression or, in other words may be in a relaxed state. 141 maintains the outer valve member c against its seat a .While the inner valve member d may be Spaced outwardly from its seat b, due to the compression spring 140"maintaining the shoulder 137 ,of the Outer valve plunger 132 against the restricted outer end of the sleeve 136; It is apparent that air could then be exhausted from the cylinder 102 of the variable speed .pulley assembly 61 so the lefiective diameter of (the pulleys A, B would be substantially less than that shown in Figure 5. Of course, the minimum diameter of these pulleys may be determined by adjustment of the screw 1,35 inthe right-hand portion of Figure 4, which would cause the'inner plunger .133 to seat against the valve member d before the pressure exhausted from the cylinder 102 was lowered to atmospheric pressure.

In any event, when the inner valve member d is "spaced from the valve seat b, air may flow from the cylinder 102, through fitting 110 and conduit 115, through passageway e, through the right-hand portion of the sleeve 136', 'past the valve member a, through the hollow inner valve plunger 133, through the exhaust port .k to be finally exhausted through the exhaust opening 143'in the housing part 131 of the pressure regulator valve 120. The air will be, exhausted from the cylinder 102 until itTeaches atmospheric pressure or 'until the pressure acting against the left-hand side 'of diaphragm '129 and plunger 133 decreases to the extent that the seat b of the inner plunger '133 is moved against the'inner valve member [I by the compression spring 134. l

When the valve control lever 150 is moved in a clockwise direction in Figure 4, this moves the outer valve plunger 132 inwardly 'toward'the' inner valve plunger 133'until the ballor inner 'valve'member d seats against its valve-seat 'b. 'Thereupon, the valve-seat a moves away from the outer valve member c with further movement "ofthe outer valve plunger 132, and this movement of the valve seat a away'irom the outer. valve meniber'c is gradual in accordance with the rateof, movement of, the valve control'lever 150. As the valveseata'moves'away from the outer valve member c, compressed air may now from the source, through theconduit-f122", through passageway into the sleeve 136 and-,fthence, through passageways h in the reduced medial portion of the outer plunger 132, past the valve seat a, through-the ports or passageways 1', through the passageway e, through conduit 115 and fitting 110 andinto the cylinder .102. i

In the event that line pressure is greater .than :the amount of pressure desired ztolbeadmittedtothe cylinder 102 'for obtaining the desired maximum speed of the machine; that is, the desired maximum effective diameter of the pulley assembly .61, lthescrew 135 :in the righthand portion of Figure 4 may be soadjustedthahupon a predetermined amount of pressure .being ,present in the cylinder 102 and, consequently, in the rightfhand portion of the sleeve 136,, the pressure presentin the right-hand p rtion o t e sleeve 1136 ay e b s h, rel v t the ,pressureexertedby the regulator spring 134, as to Also, at this time, the spring -10 move the inner valve plunger 133 away trornthevalvemember d and permit excess pressure to. escape .frornthe pressure regulator valve 120.

The pressure exerted by the spring 134 can be adjusted by the screw 135 for only one of the above conditions and, normally, the minimum effective diameter of the variable speed pulley assembly 61 is determined by the maximum extent to which the flanges 88, may move away from the respective flanges 87, 89, as limited by the stroke of the piston 103. The maximum efiective diameter of the variable speed pulley assembly 61 may also be determined by the stroke of the piston 103, but since this may, in some instances, cause the machine to run at an excessive speed, the screw may be adjusted to regulate the maximum amount of pressure which may enter the cylinder 102 and correspondingly regulate the maximum eifective diameter of the variable speed pulley assembly 61. Of course, this maximum pressure would be determined, to some extent, by the force exerted by the tension springs 77 on the motor support.

It is thus seen that I have provided a novel method of and means for automatically increasing and decreasingv the speed of a spinning or similar machine with respec-- tive downward and upward movements of a ring rail dur ing a filling wind, and for also regulating the speed of the:

machine to obtain either a-minimum or a maximum speed of the machine, and for maintaining the speed of the ma,- chine constant during the building of the bunches on the lower portions of straight bobbins during a predeter mined number of reciprocations of the ring rails following initiation of each package-winding cycle of the ma h In the drawings and specification there has been set forth a preferred embodiment of the invention and, .31;- though specific terms are employed, theyare used in a genericand descriptive sense only and not for purposes of limitation, the scope of the invention being definedin the claims. 7 V

I claim: 7

1. A spinning machine having spindles and a recipro eating .ring rail, a builder motion for reciprocating said rail and including areciprocating arm, .a main shaft adapted to rotate said spindles and to drive said builder motion, a fluid-pressure-operated variable speed drive for driving said main shaft, a pressure regulator valve interposed in a fluid pressure system to said drive, and means operatively connecting the reciprocating arm to said valve and so arranged as to close said valve with each movement in one direction and to open said valve with each movement in the other direction to thereby decrease the speed of the machine with each movement of the ring rail inone direction and increase the speed of the. machine with each movement of the ring rail in the opposite direction. I i v 1 2. A textile machine having spindles and at least one ring rail, means for driving the spindles and reciprocating the rail, pneumatically actuated means for regulating the :speed of the spindles and the ring rail, a valve adapted to produce variation of pressure in said pneumatically actuated means, and means responsive to movement of ,said rail .in one direction for opening said valve and being responsive to movement of said ,rail in the opposite ated means, and means responsive to movement ofsa-idfl rail in one direction forgradually openingsaid valve andi the oppo being responsive to movement of said rail in site direction to gradually .close said valve.

4. A textile machine having spindles, at least one ring rail, a builder motion having a reciprocatory arm coupledl to .said rail .for reciprocating the rail, means for driving;

mam

builder motion and said spindles, means responsive to fiuid pressure to regulate the speed of said motion and said rail, a valve adapted to produce variation of pressure at said pressure-responsive means, movable means on said valve for controlling the same, means in terconnecting the arm and the movable means whereby the arm produces an increase in pressure in said pressureresponsive means with movement in one direction, and

whereby the arm effects reduction in pressure in said pressure-responsive means with movement in the opposite direction.

5. A structure as claimed in claim 4 having yieldable means in said interconnectig means whereby the strokes of the arm may exceed in length the strokes of said movable means.

6. A structure according to claim 4 wherein said valve is provided with means independent of said movable means for governing the maximum pressure admittable to said pressure-responsive means.

7. A structure according to claim 4, wherein said valve is provided with means independent of said movable means for governing the minimum pressure at said pressure-responsive means.

8. A spinning machine having spindles and a reciprocating ring rail, a main shaft adapted to rotate said spindles and to reciprocate said rail, a driven shaft disposed adjacent said main shaft, a first pulley fixed on one of said shafts, a fiuid-pressure-operated expansible pulley mounted on the other of said shafts, at least one V-belt entrained over said pulleys, a conduit extending from a source of fluid pressure to said fluid-pressureoperated expansible pulley, means responsive to movement of said ring rail in one direction for increasing the amount of pressure directed into the fiuid-pressure-operated expansible pulley, said means being responsive to reciprocation of said ring rail in the opposite direction for decreasing the amount of pressure directed to the fluid-pressure-operated expansible pulley, and said expansible pulley being so arranged that increased pressure correspondingly changes the effective diameter of the expansible pulley and decreased pressure inversely changes the eifective diameter of the expansible pulley to thereby effect corresponding changes in the speed of the machine.

9. A spinning machine having spindles and a reciprocating ring rail, a main shaft adapted to rotate said spindles and to reciprocate said rail, a driven shaft disposed adjacent said main shaft, a first pulley fixed on one of said shafts, a fiuid-pressure-operated expansible pulley mounted on the other of said shafts, at least one V-belt entrained over said pulleys, a conduit extending from a source of fiuid pressure to said fluid-pressure-operated expansible pulley, means responsive to each movement of said ring rail in one direction for gradually increasing the amount of pressure directed into the fluidpressure-operated expansible pulley, said means being responsive to reciprocation of said ring rail in the opposite direction for gradually decreasing the amount of pressure directed to the fiuid-pressure-operated expansible-pulley, and said expansible pulley so arranged that increased pressure correspondingly changes the effective diameter of the expansible pulley and decreased pressure inversely changes the effective diameter of the expansible pulley to thereby effect corresponding changes in the speed of the machine.

10. A spinning machine having spindles and a reciprocating ring rail, a main shaft adapted to rotate said spindles and reciprocate said ring rail, a driven shaft disposed adjacent said main shaft, a first pulley fixed on one of said shafts, a fiuid-pressure-operatcd expansible pulley mounted on thet other of said shafts, at least one V-belt entrained over said pulleys, conduit means extending from a source of fluid pressure to said expansible pulley, a pressure regulator valve interposed in said "conduit means, means for opening said pressure regulai2 tor valve to correspondingly increase the amount of pres sure directed into the expansible pulley with movement of said ring rail in one direction with each reciprocation thereof, said last-named means also being operable for closing said pressure regulator valve to correspondingly decrease the amount of pressure directed into the expansible pulley with movement of said ring rail in the opposite direction with each reciprocation thereof, and said expansible pulley being so arranged that increased pressure increases the effective diameter of the pulley and decreased pressure decreases the effective diameter of the pulley and thereby respectively increases and decreases the speed of the machine.

11. A spinning machine having spindles and at least one reciprocating ring rail, a main shaft adapted to rotate said spindles and reciprocate said ring rail in a filling wind, a driven shaft disposed adjacent said main shaft, a first pulley fixed on one of said shafts, a fluid-pressureoperated expansible pulley mounted on the other of said shafts, at least one V-belt entrained over said pulleys, conduit means extending from a source of fluid pressure to said expansible pulley, a pressure regulator valve interposed in said conduit means, means for gradually opening said pressure regulator valve to gradually increase the amount of pressure directed into the expansible pulley with each movement of said ring rail in one direction, said last-named means also being operable for gradually closing said valve to gradually decrease the amount of pressure in the expansible pulley with each intervening movement of said ring rail in the opposite direction, and said expansible pulley being so arranged that increased pressure increases the effective diameter of the pulley and decreased pressure decreases the effective diameter of the pulley and thereby respectively increases and decreases the speed of the machine.

12. A textile machine having spindles and at least one ring rail, means for driving the spindles and reciprocating the rail, pneumatically actuated means for regulating the speed of the spindles and the ring rail, a first valve adapted to produce variation in pressure in said pneumatically actuated means, means responsive to movement of said rail in one direction for gradually opening said valve and being responsive to movement of said rail in the opposite direction to gradually close the valve, and means to render said valve ineffective during certain successive reciprocations of said rail.

13. A textile machine having spindles and at least one ring rail, means for driving the spindles and reciprocating the ring rail, pneumatically actuated means for regulating the speed of the spindles and the ring rail, a first valve adapted to produce variation in pressure in said pneumatically actuated means, means responsive to movement of said rail in one direction for opening said valve and being responsive to movement of said rail in the opposite direction to close said valve, and a second valve for rendering said valve ineifective during a predetermined number of reciprocations of the ring rail occurring upon initiation of each cycle in the operation of the machine and to thereby maintain the speed of the spindles and rail constant during the latter reciprocations.

14. A spinning machine having spindles and a reciprocating ring rail, a builder motion for reciprocating said ring rail and including a reciprocating arm, a main shaft adapted to rotate said spindles and to drive said builder motion, a fiuid-pressure-operated variable speed drive for driving said main shaft, means to maintain the pressure in said variable speed drive substantially constant during a predetermined number of reciprocations of said ring rail upon the initiation of a winding cycle in the operation of the machine, and means operable thereafter for gradually increasing the amount of pressure in said variable speed drive with each movement of the ring rail in one direction and for decreasing the pressure in said variable speed drive with each movement of the ring rail in the other direction throughout the remainder of the corresponding cycle of the machine.

15. A structure according to claim 14 wherein said last-mentioned means includes a pressure regulator valve interposed in a fluid pressure system to said drive, means operatively connecting the reciprocating arm to said valve and so arranged as to close said valve with each movement of the arm in one direction and to open said valve with each movement in the other direction, and said firstmentioned means comprises a normally closed second valve interposed in said fluid pressure system with means responsive to a predetermined number of movements of said reciprocating arm, following initiation of a winding cycle, for opening said second valve, and said second valve being arranged to exhaust pressure from the variable speed drive when closed whereby, when the second valve is open, the pressure regulator valve determines the amount of pressure in the variable speed drive.

the yarn carrier and the traversing means, valve means adapted to produce variation of pressure in said fluidpressure-operated means, and means responsive to movement of said traversing means in one direction for opening said valve means and being responsive to movement of said traversing means in the opposite direction to close said valve means.

18. In a machine having means for traversing yarn onto a rotating yarn carrier in a reciprocatory manner while maintaining the strokes of the traversing means substantially constant and progressively advancing the traversing means in one direction to form a filling-wound package on the carrier, the combination therewith of fluid-pressure-operated means for regulating the speed of the yarn carrier and the traversing means, valve means adapted to produce variation of pressure in said fluidpressure-operated means, and means responsive to move- 16. A structure according to claim 15 wherein said 7 second valve is in the form of a normally closed solenoid operated valve, a normally open switch interposed in an electrical circuit to said second valve, and means operable automatically upon a predetermined number of reciprocations of said arm, following initiation of a winding cycle, for closing said switch'to open said second valve.

17. In a machine having means for traversing yarn onto a rotating yarn carrier in a reciprocatory manner while maintaining the strokes of the traversing means substantially constant and progressively advancing the traversing means in one direction to form a filling-wound package on the carrier, the combination therewith of fiuid-pressure-operated means for regulating the speed of ment of said traversing means in one direction for gradually opening said valve means and being responsive to movement of said traversing means in the opposite direction to gradually close said valve means.

References Cited in the file of this patent UNITED STATES PATENTS 1,192,704 Stobe July 25, 1916 1,479,177 Hallock et al Jan. 1, 1924 2,507,904 Heller et al. May 16, 1950 2,803,107 Long Aug. 20, 1957 FOREIGN PATENTS 712,012 Great Britain July 14, 1954 

